Peak demand response operation with improved sensible capacity

ABSTRACT

An HVAC system includes a variable-speed compressor which compresses refrigerant flowing through the HVAC system, a blower which provides a flow of air through the HVAC system at a controllable flow rate, and a controller communicatively coupled to the variable-speed compressor and the blower. The controller receives a demand request, which includes a command to operate the HVAC system at a predefined setpoint temperature. In response to receiving the demand request, a setpoint temperature associated with the HVAC system is adjusted to the predefined setpoint temperature. The variable-speed compressor is adjusted to a low-speed setting, thereby operating the HVAC system at a first tonnage of cooling. The rate of the flow of air provided by the blower is adjusted to a first flow rate, such that a ratio of the first flow rate to the first tonnage of cooling is increased to a first predefined value.

TECHNICAL FIELD

The present disclosure relates generally to heating, ventilation, andair conditioning (HVAC) systems and methods of their use. In certainembodiments, the present disclosure relates to peak demand responseoperation with improved sensible capacity.

BACKGROUND

Heating, ventilation, and air conditioning (HVAC) systems are used toregulate environmental conditions within an enclosed space. Air iscooled via heat transfer with refrigerant flowing through the HVACsystem and returned to the enclosed space as conditioned air.

SUMMARY OF THE DISCLOSURE

In an embodiment, an HVAC system includes a variable-speed compressorconfigured to compress refrigerant flowing through the HVAC system, ablower configured to provide a flow of air through the HVAC system at acontrollable flow rate, and a controller communicatively coupled to thevariable-speed compressor and the blower. The controller receives ademand request, which includes a command to operate the HVAC system at apredefined setpoint temperature. In response to receiving the demandrequest, a setpoint temperature associated with the HVAC system isadjusted to the predefined setpoint temperature. The variable-speedcompressor is adjusted to a low-speed setting, thereby operating theHVAC system at a first tonnage of cooling corresponding to the decreasedspeed of the variable-speed compressor. The rate of the flow of airprovided by the blower is adjusted to a first flow rate, such that aratio of the first flow rate to the first tonnage of cooling isincreased to a first predefined value.

In another embodiment, an HVAC system includes a variable-speedcompressor configured to compress refrigerant flowing through the HVACsystem, a blower configured to provide a flow of air through the HVACsystem at a controllable flow rate, and a controller communicativelycoupled to the variable-speed compressor and the blower. The controlleris configured to receive a demand request, which includes a command tooperate the HVAC system at a predefined setpoint temperature. Inresponse to receiving the demand request, a setpoint temperatureassociated with the HVAC system is adjusted to the predefined setpointtemperature. A speed of the variable-speed compressor is decreased to alow-speed setting. Based on the decreased speed of the variable-speedcompressor, an air-flow rate is determined to provide by the blower. Thecontrollable flow rate of the flow of air provided by the blower isadjusted based on the determined air-flow rate.

In yet another embodiment, an HVAC system includes a cooling unit with aface-split evaporator. The face-split evaporator includes a topevaporator circuit positioned above a bottom evaporator circuit. The topevaporator circuit is configured to transfer heat from a first portionof a flow of air passing across the top evaporator circuit torefrigerant in the top evaporator circuit. The bottom evaporator circuitis configured to transfer heat from a second portion of the flow of airpassing across the bottom evaporator circuit to refrigerant in thebottom evaporator circuit. The system further includes a firstcompressor associated with the top evaporator circuit and configured tocompress refrigerant received from the top evaporator circuit, a secondcompressor associated with the bottom evaporator circuit and configuredto compress refrigerant received from the bottom evaporator circuit, anda controller communicatively coupled to the first compressor and thesecond compressor. The controller receives a demand request, whichincludes a command to reduce power consumption by the HVAC system by apredefined percentage. In response to receiving the demand request, thesecond compressor is turned off to inactivate the bottom evaporatorcircuit such that power consumption by the HVAC system is decreased byat least the predefined percentage associated with the demand request. Afirst portion of a liquid condensate formed on a surface of the topevaporator circuit is allowed to fall on a surface of the bottomevaporator circuit such that the second portion of the flow of air isevaporatively cooled by the first portion of the liquid condensate.

In some cases, HVAC systems may be required to operate under restrictedoperating requirements to reduce power consumption during times of peakelectricity demand, referred to in this disclosure as peak demandresponse times. For example, a third party such as a utility providermay enforce certain operating restrictions upon HVAC systems during peakdemand response times. A peak demand response time may correspond, forexample, to a time period associated with high outdoor temperatures orany other time when electrical power consumption is expected (e.g.,based on a forecast or projection) to be increased. Generally, the thirdparty (e.g., a utility provider) provides a command request whichspecifies either a setpoint temperature or a reduction of powerconsumption at which an HVAC system should operate during a peak demandresponse time. In some cases, the demand request may be provided via anelectronic signal. The demand request may be transmitted to a controllerof the HVAC system to communicate operating requirements that are to beenforced during a peak demand response time.

The unconventional HVAC systems contemplated in the present disclosuresolve problems of previous systems by facilitating improved coolingduring a peak demand response time (e.g., by increasing sensiblecapacity during the peak demand response time). The present disclosureencompasses the recognition that the sensible capacity of HVAC systemsmay be increased during peak demand response times by temporarilymodifying operating parameters of the HVAC system to improve comfort ina conditioned space while still satisfying the requirements of a demandrequest. For example, a speed of a compressor of the HVAC system may betemporarily decreased to increase a sensible heat ratio of the HVACsystem and improve the sensible capacity of the HVAC system during apeak demand response time. In this way the HVAC system may continue toeffectively cool a space while still satisfying requirements of a demandrequest (e.g., to increase a setpoint temperature or reduce powerconsumption by a given percentage). In some embodiments, the systems andmethods described in this disclosure are configured to exploit thebenefits of evaporative cooling to provide improved sensible capacity,and thereby provide more comfortable temperatures during peak demandresponse times than was possible using previous technologies. Moreover,the systems and methods described in this disclosure may be integratedinto a practical application for improving the performance and sensiblecooling capacity of HVAC systems during peak demand response times.

Certain embodiments may include none, some, or all of the abovetechnical advantages. One or more other technical advantages may bereadily apparent to one skilled in the art from the figures,descriptions, and claims included herein.

BRIEF DESCRIPTION OF THE DRAWINGS

For a more complete understanding of the present disclosure, referenceis now made to the following description, taken in conjunction with theaccompanying drawings, in which:

FIG. 1 is a diagram of an example HVAC system configured for operationaccording to a demand request;

FIG. 2 is a plot of HVAC operating metrics versus compressor speed foran example HVAC system;

FIGS. 3A-B are flowcharts illustrating example methods of operating anHVAC system of FIG. 1;

FIG. 4 is a flowchart illustrating a further example method of operatingthe HVAC system of FIG. 1;

FIG. 5 is a diagram of an example face-split evaporator for use in thesystem of FIG. 1;

FIG. 6 is a flowchart of an example method of operating the HVAC systemof FIG. 1 employing the face-split evaporator of FIG. 5 to improvesensible capacity during a peak demand response time; and

FIG. 7 is a diagram of the controller of the example HVAC system of FIG.1.

DETAILED DESCRIPTION

Embodiments of the present disclosure and its advantages are bestunderstood by referring to FIGS. 1 through 7 of the drawings, likenumerals being used for like and corresponding parts of the variousdrawings.

The extent of cooling and dehumidification an HVAC system can achieve isgenerally determined by its sensible capacity (Sc) and latent capacity(Lc). Each HVAC system has a total capacity (Tc), which is the sum ofthe sensible capacity and latent capacity (i.e., Tc=Sc+Lc). Generally,sensible capacity refers to an ability of the HVAC system to removesensible heat from conditioned air (i.e., to cool the air). As usedherein, sensible heat refers to heat that, when added to or removed fromthe air, results in a temperature change of the conditioned air.Comparatively, latent heat refers to the ability of an HVAC system toremove latent heat from conditioned air (i.e., to dehumidify the air).As used herein, latent heat refers to heat that, when added to orremoved from the conditioned air, results in a phase change of, forexample, water within the conditioned air. Sensible capacity and latentcapacity may vary with environmental conditions.

HVAC systems are generally operated to achieve a sensible heat ratio(“SIT ratio”), where S/T ratio=Sc/Tc, of about 0.75. For the example ofa 0.75 S/T ratio, an HVAC system is devoting 75% of its total capacityto removing sensible heat (i.e., for cooling) and 25% of its totalcapacity to remove latent heat (i.e., for dehumidification). Generally,an increased S/T ratio relative to this value is associated with anincrease in the humidity of the conditioned air, while a decreased S/Tratio is associated with dehumidification of the conditioned air.

The S/T ratio generally changes proportionally with the ratio of theflow rate of air provided by the blower to the tonnage of the HVACsystem (i.e., the “CFM/ton” of the HVAC system). The flow rate of airprovided by the blower is generally measured in units of cubic feet perminute (CFM). The tonnage of the HVAC system corresponds to the coolingcapacity of the system, where one “ton” of cooling corresponds to 12000Btu/hr. The tonnage of the HVAC system is largely determined by thespeed of the compressor(s) of the system, such that a decreasedcompressor speed corresponds to a decreased tonnage. The relationshipbetween compressor speed and system tonnage is approximately linear.Accordingly, the CFM/ton value of an HVAC system, and thus theassociated S/T Ratio, may be controlled by adjusting the flow rate ofair provided by the blower and/or the tonnage of the HVAC system. Forexample, at a constant air flow rate from the blower, the speed of avariable-speed compressor may be decreased, to increase the CFM/tonvalue and the associated S/T Ratio of the system.

As described above, prior to the present disclosure, there was a lack oftools for improving comfort in a conditioned space in response to ademand request. This disclosure encompasses the unique recognition thatthe S/T ratio or the CFM/ton of an HVAC system can be increased to moreeffectively maintain comfortable temperatures in a conditioned spaceduring a peak demand response time while still fulfilling therequirements of an associated demand request (e.g., to operate at apredefined setpoint temperature or at a reduced power consumption). Forexample, the temperature in a conditioned space may increase lessrapidly during a peak demand response time when the efficiency modesdescribed in this disclosure are employed.

HVAC System

FIG. 1 is a schematic diagram of an embodiment of an HVAC system 100configured for operation during a peak demand response time. The HVACsystem 100 conditions air for delivery to a conditioned space. Theconditioned space may be, for example, a room, a house, an officebuilding, a warehouse, or the like. In some embodiments, the HVAC system100 is a rooftop unit (RTU) that is positioned on the roof of a buildingand the conditioned air is delivered to the interior of the building. Inother embodiments, portion(s) of the system may be located within thebuilding and portion(s) outside the building. The HVAC system mayinclude one or more heating elements, not shown for convenience andclarity. The HVAC system 100 may be configured as shown in FIG. 1 or inany other suitable configuration. For example, the HVAC system 100 mayinclude additional components or may omit one or more components shownin FIG. 1.

The HVAC system 100 includes a working-fluid conduit subsystem 102, atleast one condensing unit 104, an expansion valve 114, a cooling unit116, a thermostat 132, and a controller 136. The HVAC system 100 isgenerally configured to operate at an increased sensible capacity when ademand request 138 is received from third part 140 which indicates thatthe HVAC system 100 is required to operate under conditions associatedwith decreased power consumption. For example, the demand request 138may indicate that the HVAC system 100 must be operated at a predefinedsetpoint temperature (e.g., a setpoint temperature that is higher thanmay be preferred for comfort to occupants of a space conditioned by theHVAC system 100) or at a predefined percentage reduction of powerconsumption during a peak demand response time. In response to thedemand request 138, the HVAC system 100 is operated according to anefficiency mode, illustrative examples of which are described in greaterdetail below, which provides improved cooling during the peak demandresponse time than was possible using previous technologies, while stillsatisfying operating requirements associated with the demand request138.

The working fluid conduit subsystem 102 facilitates the movement of aworking fluid (e.g., a refrigerant) through a cooling cycle such thatthe working fluid flows as illustrated by the dashed arrows in FIG. 1.The working fluid may be any acceptable working fluid including, but notlimited to, fluorocarbons (e.g. chlorofluorocarbons), ammonia,non-halogenated hydrocarbons (e.g. propane), hydroflurocarbons (e.g.R-410A), or any other suitable type of refrigerant.

The condensing unit 104 includes a compressor 106, a condenser 108, anda fan 110. In some embodiments, the condensing unit 104 is an outdoorunit while other components of system 100 may be indoors. The compressor106 is coupled to the working-fluid conduit subsystem 102 and compresses(i.e., increases the pressure of) the working fluid. The compressor 106of condensing unit 104 may be a variable-speed or multi-stagecompressor. A variable-speed compressor is generally configured tooperate at different speeds to increase the pressure of the workingfluid to keep the working fluid moving along the working-fluid conduitsubsystem 102. In the variable-speed compressor configuration, the speedof compressor 106 can be modified to adjust the cooling capacity of theHVAC system 100. Meanwhile, a multi-stage compressor may includemultiple compressors, each configured to operate at a constant speed toincrease the pressure of the working fluid to keep the working fluidmoving along the working-fluid conduit subsystem 102. In the multi-stagecompressor configuration, one or more compressors can be turned on oroff to adjust the cooling capacity of the HVAC system 100. As describedin greater detail below with respect to FIG. 5, in certain embodiments,the HVAC system 100 may include two or more condensing units (e.g.,condensing units 506 and 512 of FIG. 5).

The compressor 106 is in signal communication with the controller 136using wired or wireless connection. The controller 136 provides commandsor signals to control operation of the compressor 106 and/or receivessignals from the compressor 106 corresponding to a status of thecompressor 106. For example, when the compressor 106 is a variable-speedcompressor, the controller 136 may provide signals to control thecompressor speed. When the compressor 106 operates as a multi-stagecompressor, the signals may correspond to an indication of whichcompressors to turn on and off to adjust the compressor 106 for a givencooling capacity. The controller 136 may operate the compressor 106 indifferent modes corresponding to load conditions (e.g., the amount ofcooling or heating required by the HVAC system 100). As described ingreater detail below, operation of the compressor 106 may be adjusted bythe controller 136 before, during, and/or after a peak demand responsetime to increase the sensible capacity of the HVAC system 100 during apeak demand response time. The controller 136 is described in greaterdetail below with respect to FIG. 7.

The condenser 108 is configured to facilitate movement of the workingfluid through the working-fluid conduit subsystem 102. The condenser 108is generally located downstream of the compressor 106 and is configuredto remove heat from the working fluid. The fan 110 is configured to moveair 112 across the condenser 108. For example, the fan 110 may beconfigured to blow outside air through the condenser 108 to help coolthe working fluid flowing there through. The compressed, cooled workingfluid flows from the condenser 108 toward an expansion device 114.

The expansion device 114 is coupled to the working-fluid conduitsubsystem 102 downstream of the condenser 108 and is configured toremove pressure from the working fluid. In this way, the working fluidis delivered to the cooling unit 116 and receives heat from airflow 118to produce a conditioned airflow 120 that is delivered by a ductsubsystem 122 to the conditioned space. In general, the expansion device114 may be a valve such as an expansion valve or a flow control valve(e.g., a thermostatic expansion valve valve) or any other suitable valvefor removing pressure from the working fluid while, optionally,providing control of the rate of flow of the working fluid. Theexpansion device 114 may be in communication with the controller 136(e.g., via wired and/or wireless communication) to receive controlsignals for opening and/or closing associated valves and/or provide flowmeasurement signals corresponding to the rate of working fluid flowthrough the working fluid subsystem 102.

The cooling unit 116 is generally any heat exchanger configured toprovide heat transfer between air flowing through the cooling unit 116(i.e., air contacting an outer surface of one or more coils of thecooling unit 112) and working fluid passing through the interior of thecooling unit 116. For example, the cooling unit 116 may be or include anevaporator coil. More specifically, the cooling unit 116 may be orinclude a row/split intertwined evaporator (e.g., as described ingreater detail below with respect to FIG. 4) or a face-split evaporator(e.g., as described in greater detail below with respect to FIGS. 5 and6). The cooling unit 116 is fluidically connected to the compressor 106,such that working fluid generally flows from the cooling unit 116 to thecondensing unit 104. A portion of the HVAC system 100 is configured tomove air 118 across the cooling unit 116 and out of the duct sub-system122 as conditioned airflow 120. Return air 124, which may be airreturning from the building, fresh air from outside, or somecombination, is pulled into a return duct 126.

A suction side of a blower 128 pulls the return air 124. The blower 128discharges airflow 118 into a duct 130 such that airflow 118 crosses thecooling unit 116 or heating elements (not shown) to produce conditionedairflow 120. The blower 128 is any mechanism for providing a flow of airthrough the HVAC system 100. For example, the blower 128 may be aconstant-speed or variable-speed circulation blower or fan. Examples ofa variable-speed blower include, but are not limited to, belt-driveblowers controlled by inverters, direct-drive blowers with electroniccommuted motors (ECM), or any other suitable type of blower. The blower128 is in signal communication with the controller 136 using anysuitable type of wired or wireless connection. The controller 136 isconfigured to provide commands and/or signals to the blower 128 tocontrol its operation. For example, the controller 136 may be configuredto send signals to the blower 128 to adjust the speed of the blower 128,for example, to increase the cooling capacity of the HVAC system 100during a peak demand response time, as described in greater detailbelow.

The HVAC system 100 includes one or more sensors 130 a-b in signalcommunication with the controller 136. The sensors 130 a-b may includeany suitable type of sensor for measuring air temperature, relativehumidity, and/or any other properties of a conditioned space (e.g. aroom or building). The sensors 130 a-b may be positioned anywhere withinthe conditioned space, the HVAC system 100, and/or the surroundingenvironment. For example, as shown in the illustrative example of FIG.1, the HVAC system 100 may include a sensor 130 a positioned andconfigured to measure a return air temperature (e.g., of airflow 124)and/or a sensor 130 b positioned and configured to measure a supply ortreated air temperature (e.g., of airflow 120), a temperature of theconditioned space, and/or a relative humidity of the conditioned space.In other examples, the HVAC system 100 may include sensors positionedand configured to measure any other suitable type of air temperature(e.g., the temperature of air at one or more locations within theconditioned space and/or an outdoor air temperature) or other property(e.g., a relative humidity of air at one or more locations within theconditioned space).

The HVAC system 100 includes a thermostat 132, for example, locatedwithin the conditioned space (e.g. a room or building). The thermostat132 is generally in signal communication with the controller 136 usingany suitable type of wired or wireless connection. The thermostat 132may be a single-stage thermostat, a multi-stage thermostat, or anysuitable type of thermostat as would be appreciated by one of ordinaryskill in the art. The thermostat 132 is configured to allow a user toinput a desired temperature or temperature setpoint 134 of theconditioned space for a designated space or zone such as a room in theconditioned space. The controller 136 may use information from thethermostat 132 such as the temperature setpoint 134 for controlling thecompressor 106 and/or the blower 128. In some embodiments, thethermostat 132 includes a user interface for displaying informationrelated to the operation and/or status of the HVAC system 100. Forexample, the user interface may display operational, diagnostic, and/orstatus messages and provide a visual interface that allows at least oneof an installer, a user, a support entity, and a service provider toperform actions with respect to the HVAC system 100. For example, theuser interface may provide for input of the temperature setpoint 134 anddisplay of any alerts and/or messages related to the status and/oroperation of the HVAC system 100.

As described in greater detail below, the controller 136 is configuredto receive a demand request 138 from a third party 140. The demandrequest 138 may correspond to information transmitted via an electronicsignal from the third party 140. Generally, the controller 136 isconfigured to receive and interpret the demand request 138 and toappropriately adjust operation of the HVAC system 100 to satisfyoperating requirements associated with the demand request 138. Thedemand request 138 is generally associated with a time interval (e.g., astart and stop time) during which certain operating requirements shouldor must be enforced for the HVAC system 100. The time interval of thedemand request 138 may correspond to a peak demand response time (e.g.,a time during which electrical power consumption should be decreased).The operating requirements of the demand request 138 may be associatedwith a predefined setpoint temperature (i.e., a value at which thetemperature setpoint 134 must be set during the time interval), anamount (e.g., a percentage) by which the HVAC system 100 must decreaseits power consumption, an amount of power that can be consumed by theHVAC system 100, or the like. In general, the demand request 138 mayinclude any appropriate demand requirement associated with decreasingpower consumed by the HVAC system 100, as would be appreciated by aperson skilled in the art. The third party 140, which provides thedemand request 138, may be a utility provider or any other entity withadministrative privileges over operation of the HVAC system 100.

As described above, in certain embodiments, connections between variouscomponents of the HVAC system 100 are wired. For example, conventionalcable and contacts may be used to couple the controller 136 to thevarious components of the HVAC system 100, including, the compressor106, the expansion valve 114, the blower 128, sensor(s) 130 a-b, andthermostat(s) 132. In some embodiments, a wireless connection isemployed to provide at least some of the connections between componentsof the HVAC system 100. In some embodiments, a data bus couples variouscomponents of the HVAC system 100 together such that data iscommunicated therebetween. In a typical embodiment, the data bus mayinclude, for example, any combination of hardware, software embedded ina computer readable medium, or encoded logic incorporated in hardware orotherwise stored (e.g., firmware) to couple components of HVAC system100 to each other. As an example and not by way of limitation, the databus may include an Accelerated Graphics Port (AGP) or other graphicsbus, a Controller Area Network (CAN) bus, a front-side bus (FSB), aHYPERTRANSPORT (HT) interconnect, an INFINIBAND interconnect, alow-pin-count (LPC) bus, a memory bus, a Micro Channel Architecture(MCA) bus, a Peripheral Component Interconnect (PCI) bus, a PCI-Express(PCI-X) bus, a serial advanced technology attachment (SATA) bus, a VideoElectronics Standards Association local (VLB) bus, or any other suitablebus or a combination of two or more of these. In various embodiments,the data bus may include any number, type, or configuration of databuses, where appropriate. In certain embodiments, one or more data buses(which may each include an address bus and a data bus) may couple thecontroller 136 to other components of the HVAC system 100.

In an example operation of HVAC system 100, the HVAC system 100 startsup to provide cooling to an enclosed space based on temperature setpoint134. For example, in response to the indoor temperature exceeding thetemperature setpoint 134, the controller 136 may cause the compressor106 and the blower 128 to turn on to startup the HVAC system 100. TheHVAC system 100 is generally operated in a normal cooling mode (e.g.,associated with a CFM/ton value in a range from about 400 to 450 CFM/tonor an S/T ratio in a range from about 0.7 to 0.75). Upon receipt of ademand request 138, the controller 136 may determine a start time andoperating requirements of the demand request 138. For example, thecontroller may determine, based on the demand request 138, that the HVACsystem must be operated according to certain energy-saving requirements(e.g., at a particular setpoint temperature or at a particularpercentage of the current power consumption) starting at a predefinedtime in the future and lasting for predefined time intervalcorresponding to a peak demand response time. The present disclosurecontemplates various efficiency modes in which to operate the HVACsystem 100 in order to provide more comfortable (e.g., cooler)temperatures than could be achieved during a peak demand response timeusing previous technologies. Each efficiency mode generally facilitatesoperation at an increased sensible capacity while still satisfying theoperating requirements associated with the demand request 138.

For example, if the demand request 138 includes a requirement to operatethe HVAC system at a predefined setpoint temperature, the controller 136may cause the temperature setpoint 134 to be set to this predefinedsetpoint temperature. In general, the predefined setpoint temperature isa temperature value that is greater than would generally be preferredfor the comfort of individuals occupying a space conditioned by the HVACsystem 100. For example, in some embodiments, the predefined setpointtemperature is 77° F. or greater. In some embodiments, the controller136 may cause the speed of the compressor 106 to be decreased. The speedof the blower 128 may then be adjusted to a value based on an efficiencymode CFM/ton value (e.g., to values in a range from about 500-700CFM/ton, as described with respect to the first efficiency modeillustrated in FIG. 3B below) or based on a calculated value (e.g., asdescribed with respect to the second efficiency mode illustrated in FIG.4 below). In some embodiments, the controller 136 may employ a feedbackloop to determine and set the speeds of the compressor 106 and/or blower128 based on a measured temperature of the conditioned space (e.g., asalso described with respect to the second efficiency mode illustratedFIG. 4 below). For example, speeds for the compressor 106 and/or theblower 128 may be established to increase any one or more of the coolingcapacity of the HVAC system 100, the efficiency of the HVAC system 100,or any other appropriate performance metric of the HVAC system 100.

As another example, if the demand request 138 includes a requirement tooperate the HVAC system 100 at a predefined percentage of current powerconsumption (e.g., or a predefined percentage of maximum powerconsumption) for the HVAC system 100, the controller 136 may adjust thespeed of the compressor 106 such that the required percentage of powerconsumption is obtained. The controller 136 will further (i.e., whilestill maintaining the percentage of power consumption required by thedemand response 138) adjust the speeds of the compressor 106 and/orblower 128 to values that achieve an efficiency mode CFM/ton value(e.g., to values in a range from about 500-700 CFM/ton, as describedwith respect to the first efficiency mode illustrated in FIG. 3B below).The speed of the blower 128 may alternatively be determined and setbased on a calculated value and/or via a feedback control loop (e.g., asdescribed with respect to the second efficiency mode illustrated in FIG.4 below), while satisfying the required power reduction of the demandrequest 138.

In some embodiments, the cooling unit 116 includes a face-splitevaporator which includes a top circuit positioned above a bottomcircuit (e.g., as described with respect to FIG. 5 below). In suchembodiments, the controller 136 may implement a third efficiency mode ofoperation and cause, in response to receiving the demand request 138,the bottom evaporator circuit to act as an evaporative cooler, forexample, by deactivating a compressor associated with this circuit(e.g., a compressor that provides a flow of working fluid through thebottom circuit). As described in greater detail below with respect toFIGS. 5 and 6, deactivating the bottom circuit of the face-splitevaporator may provide improved sensible capacity during the demandresponse time associated with the demand request 138.

FIG. 2 shows an example plot 200 demonstrating certain benefits of thesystems and methods described in this disclosure. The plot 200 includesvalues of the percentage of total power consumed 202, the CFM/ton value204 during normal cooling mode operation of the HVAC system, thecorresponding sensible capacity 206 during cooling mode operation, theadjusted CFM/ton value208 during an example efficiency mode operation,and the corresponding sensible capacity 210 during efficiency modeoperation. The total power consumed 202 generally decreases withdecreasing compressor speed. During cooling mode operation, the CFM/tonvalue 204 (e.g., or an associated S/T ratio) remains approximatelyconstant at a value near 400 to 450 CFM/ton, and the sensible capacity206 decreases relatively sharply with decreasing compressor speed. Incontrast, during efficiency mode operation, the CFM/ton value 208 (e.g.,or an associated S/T ratio) is increased, and the corresponding sensiblecapacity 210 decreases less rapidly with decreasing compressor speed.

As further illustrated in FIG. 2, if a 48% reduction of total powerconsumption 202 is enforced by a demand request 138, the compressorspeed is decreased to an appropriate speed of 30 Hz to achieve thispower reduction. The sensible capacity 206 achieved during normalcooling mode operation at 30 Hz compressor speed decreases by about 42%.Meanwhile, for the same 48% reduction of total power consumption 202(i.e., at a compressor speed of 30 Hz), the sensible capacity 210 duringefficiency mode operation only decreases by about 23%. Because theefficiency-mode sensible capacity 210 is maintained nearer its originalvalue (i.e., with a smaller percent reduction of 23% vs. 48%),efficiency mode operation provides improved cooling compared to thatpossible using conventional cooling strategies of previous technologies.Since an increase in the sensible capacity is generally associated witha corresponding decrease in latent capacity, in some embodiments, thecontroller may cause the HVAC system 100 to operate in adehumidification mode prior to operating in the various efficiency modesdescribed below (e.g., to help maintain the conditioned space at or neara desired relative humidity value during a peak demand response time).

First Efficiency Mode Operation Based on Operating at a PredefinedCFM/Ton Value

FIGS. 3A-B are flowcharts illustrating example methods 300, 350 ofoperating the HVAC system 100 of FIG. 1 in response to receiving ademand request 138. The method 300 generally includes initial stepswhich may be performed following receipt of a demand request 138 andbefore different process flows are executed based on whether the demandrequest 138 is associated with setting a required setpoint temperature(leading to steps 316, 402, and 602 of FIGS. 3B, 4, and 6, respectively)or reducing power consumption (leading to steps 334, 422, and 608 ofFIGS. 3B, 4, and 6, respectively). As such, the method 300 may includepreliminary steps that precede any of the methods described in thisdisclosure including those described with respect to FIGS. 3B, 4, and 6below.

The method 300 may begin at step 302 where the controller 136 determineswhether there is an upcoming demand requirement (e.g., a requirement foroperating the HVAC system 100 at a predefined setpoint temperature or ata predefined percentage of power consumption based on a received demandrequest 138). If there is no upcoming demand requirement, the method 300may return to start to continue monitoring for an upcoming demandrequirement (e.g., based on the receipt of a demand request 138).

If an upcoming demand requirement is identified at step 302, thecontroller 136 determines, at step 304, whether to dehumidify theconditioned space prior to the start of the peak demand response timeassociated with the demand request 138. For example, the controller 136may receive a relative humidity measurement associated with theconditioned space from sensor 130 b and/or any other sensor of the HVACsystem 100 and determine whether the measured relative humidity isgreater than a threshold value. If the relative humidity is greater thanthe threshold value then pre-dehumidification may be desired at step304, and pre-dehumidification may be performed at step 306. At step 306,pre-dehumidification may involve operating the HVAC system in adehumidification mode associated with a relatively low S/T value. Forexample, the speeds of the compressor 106 and/or the blower 128 may beadjusted to operate the HVAC system 100 at a CFM/ton value that is in arange from about 100 CFM/ton to less than 400 CFM/ton. For example, theCFM/ton value may be adjusted to a value of less than 400 CFM/ton todehumidify the conditioned space with or without providing substantialcooling to the conditioned space.

At step 308, the controller 136 determines whether the start of the peakdemand response time has been reached. The controller 136 generallycontinues to wait until this time is reached. After or upon reaching thestart of the peak demand response time, the controller 136 may determinewhether the relative humidity (RH) of the conditioned space is less thana maximum relative humidity value (RH_(max)), at step 310. If thiscriteria is not satisfied, subsequent steps associated with efficiencymode operation may not be performed. This may prevent the conditionedspace from becoming excessively or uncomfortably humid during efficiencymode operation.

Otherwise, if the criteria are satisfied at step 310, the controller 136may proceed to step 312 to determine whether the demand request 138 isassociated with a requirement to operate at a predefined setpointtemperature. If this is the case, the controller 136 may proceed to step316, 402, or 602 of FIGS. 3B, 4, and 6, respectively. If this is not thecase, the controller 136 determines whether the demand request 138 isassociated with operation at a predefined percentage reduction of powerat step 314. If this is the case, the controller 136 proceeds to step334, 422, and 608 of FIGS. 3B, 4, and 6, respectively.

FIG. 3B is a flowchart illustrating an example method 350 of operatingthe HVAC system 100 of FIG. 1 in an efficiency mode using a predefinedCFM/ton value. Method 350 may follow from step 312 or step 314 of FIG.3A, based on whether the received demand request 138 requires operationat predefined setpoint temperature (starting from step 312) or apredefined reduction of power consumption (starting from step 314), asshown in FIG. 3B.

If the demand request 138 is associated with a requirement to operatethe HVAC system 100 at a predefined setpoint temperature, the method 350may begin at step 316. At step 316, the temperature setpoint 134 isadjusted to the predefined setpoint temperature associated with thedemand request 138. For example, the demand request 138 may beassociated with a predefined (e.g., defined by the third party 140)setpoint temperature that is a particular value (e.g., 77° F. orgreater). In some cases, the predefined setpoint temperature may beprovided as an amount to increase the temperature setpoint 134. Forexample, the demand request 138 may specify a temperature differencevalue (of about 1 to 10° F.), and the temperature setpoint 134 may beincreased by the temperature difference value. At step 316, the speed ofthe compressor 106 is also decreased. For example, the compressor 106may be adjusted to operate in a low speed mode (e.g., at a speed that is75% or less of a recommended speed of the compressor 106). For example,the low speed mode may correspond to a speed of the compressor 106 ofabout 30 Hz or less. The speed of the blower 128 is adjusted such thatthe HVAC system 100 operates at an efficiency mode CFM/ton value. Theefficiency mode CFM/ton value is generally larger than the CFM/ton valueassociated with normal cooling operation (e.g., of about 400 CFM/ton).For example, the efficiency mode CFM/ton value may be in a range fromabout 500 CFM/ton to about 700 CFM/ton. Operation at an increasedCFM/ton value generally corresponds to operation at an increased S/Tratio. Operation at the efficiency mode CFM/ton value may correspond tooperation at an S/T ratio of about 0.9 or greater.

At step 318, the controller 136 determines whether a measuredtemperature (e.g., a temperature of the conditioned space or thetemperature of a zone or portion of the conditioned space) is within apredefined range of the new temperature setpoint (T_(new)) establishedat step 316. For example, the controller may determine whether themeasured temperature is greater than T_(new)−1° F. and less thanT_(new)+0.5° F. (e.g., as shown in the example of FIG. 3B). If themeasured temperature is not within this range, the controller 136proceeds to step 320 and determines whether the relative humidityassociated with the conditioned space is greater than or equal to themaximum relative humidity value. If the relative humidity value isgreater than or equal to the maximum relative humidity value, thecontroller 136 proceeds to step 322 and adjusts the speed of the blower128 such that the HVAC system 100 operates at a normal cooling modeCFM/ton value (e.g., of about 400 to 450 CFM/ton). Operation at thenormal cooling mode CFM/ton value may correspond to operation at an S/Tratio in a range from about 0.7 to about 0.75. Otherwise, if therelative humidity value is not greater than or equal to the maximumrelative humidity value, the HVAC system 100 continues to operateaccording to the efficiency mode associated with step 316.

If at step 318 the measured temperature is within the temperature rangeassociated with this step, the controller 136 proceeds to step 324. Atstep 324, the speed of the compressor 106 is increased to a medium speed(e.g., in a range from greater than 30 Hz to about 50 Hz), and the speedof the blower 128 is adjusted such that the HVAC system 100 continues tooperate according to the efficiency mode CFM/ton value (e.g. in a rangefrom about 500 CFM/ton to about 700 CFM/ton). As described above,operation at the efficiency mode CFM/ton value may correspond tooperation at an S/T ratio of about 0.9 or greater.

At step 326, the controller 136 determines whether a measuredtemperature (e.g., a temperature of the conditioned space or thetemperature of a zone or portion of the conditioned space) is greaterthan a threshold temperature (T_(threshold)). For example, the thresholdtemperature may be T_(new)+0.5° F. If the measured temperature is notgreater than the threshold temperature, the controller 136 proceeds tostep 328 and determines whether a relative humidity associated with theconditioned space is greater than or equal to the maximum relativehumidity value. If the relative humidity is greater than or equal to themaximum relative humidity value, the controller 136 proceeds to step 330and adjusts the speed of the blower 128 such that the HVAC system 100operates at a normal cooling mode CFM/ton value (e.g., of about 400 to450 CFM/ton). Otherwise, if the relative humidity is not greater than orequal to the maximum relative humidity value, the HVAC system 100continues to operate in the efficiency mode associated with step 324(i.e., at a medium compressor speed and an efficiency mode CFM/tonvalue). If at step 326 the measured temperature is greater than thethreshold temperature, the speed of the compressor 106 is set to a highspeed (e.g., a speed greater than 50 Hz, e.g., a speed of 60 Hz, e.g., amaximum recommended speed of the compressor 106) at step 332. The speedof the blower 128 is adjusted such that the HVAC system operates at anormal cooling mode CFM/ton value (e.g., of about 400 to 450 CFM/ton).

If the demand request 138 is associated with a requirement to reducepower consumption, the method 350 may begin at step 334. At step 334,the speed of the compressor 106 is decreased. For example, thecompressor 106 may be adjusted to operate in a low speed mode (e.g., ata speed of about 30 Hz or less). The speed of the blower 128 is adjustedsuch that the HVAC system 100 operates at an efficiency mode CFM/tonvalue. As described above, the efficiency mode CFM/ton value isgenerally larger than the CFM/ton value associated with normal coolingoperation (e.g., of about 400 to 450 CFM/ton). For example, theefficiency mode CFM/ton value may be in a range from about 500 CFM/tonto about 700 CFM/ton, as described above.

At step 336, the controller 136 determines whether a measured relativehumidity associated with the conditioned space is greater than or equalto the maximum relative humidity value. If the relative humidity valueis greater than or equal to the maximum relative humidity value, thecontroller 136 proceeds to step 338 and adjusts the speed of thecompressor 106 and the speed of the blower 128 such that the HVAC system100 operates at a normal cooling mode CFM/ton value (e.g., of about 400to 450 CFM/ton). At step 338, the compressor speed may be increased to amedium speed value initially (e.g., a speed in a range from greater than30 to about 50 Hz) before increasing the speed to a high speed ofgreater than 50 Hz or at a maximum recommended speed of the compressor106 (e.g., at 60 Hz). Otherwise, if at step 336 the relative humidityvalue is not greater than or equal to the maximum relative humidityvalue, the HVAC system 100 continues to operate according to theefficiency mode associated with step 334.

Modifications, additions, or omissions may be made to methods 300 and350 depicted in FIGS. 3A-B. Methods 300 and 350 may include more, fewer,or other steps. For example, steps may be performed in parallel or inany suitable order. While at times discussed as controller 136, HVACsystem 100, or components thereof performing the steps, any suitableHVAC system or components of the HVAC system may perform one or moresteps of the method.

Second Efficiency Mode Operation Based on Calculated CFM/Ton and/orFeedback Control

FIG. 4 is a flowchart of an example method 400 of operating the HVACsystem 100 of FIG. 1 in an efficiency mode using a calculated CFM/tonvalue. For example, a CFM/ton value may be calculated according to arelationship that is specific to the HVAC system 100 such thatefficiency and/or sensible capacity can be further improved during peakdemand response times. As described in greater detail below, certainsteps of method 400 may be implemented using a feedback control loop418. Method 400 may start from step 312 or step 314 of method 300 shownin FIG. 3A based on whether the received demand request 138 requiresoperation at a predefined setpoint temperature (starting from step 312of FIG. 3A) or a predefined reduction of power consumption (startingfrom step 314 of FIG. 3A). In some embodiments, the method 400 may beemployed when the cooling unit 116 of the HVAC system 100 is a rowsplit/intertwined evaporator.

If the demand request 138 is associated with a requirement to operatethe HVAC system 100 at a predefined setpoint temperature, the method 400may begin from step 312 of FIG. 3A at step 402. At step 402, thetemperature setpoint 134 is adjusted to the predefined setpointtemperature associated with the demand request 138. For example, asdescribed above, the demand request 138 may be associated with apredefined setpoint temperature that is a particular value (e.g., 77° F.or greater). In some cases, the predefined setpoint temperature may beprovided via a required increase in the temperature setpoint 134. Forexample, the demand request 138 may specify a temperature differencevalue (e.g., of about 1 to 10° F.), and the temperature setpoint 134 maybe increased by the temperature difference value.

At step 402, the speed of the compressor 106 is decreased. For example,the compressor 106 may be adjusted to operate in a low speed mode (e.g.,a speed of about 30 Hz or less). A blower speed is determined based onthe compressor speed, and the speed of the blower 128 is adjusted basedon this determined blower speed. For example, the blower speed may bedetermined using a predefined relationship between blower speed andcompressor speed (e.g., a formula, lookup table, or the like). Thepredefined relationship may facilitate operation at an increasedsensible energy efficiency ratio, a preferred (e.g., increased) S/Tratio, or the like. An example of a relationship for determining ablower speed may be: Blower speed=A(compressor speed)²+B(compressorspeed)+C, where A, B, and C are constant values. The constants A, B, andC may be specific to the HVAC system 100 and may be determined, forexample, through calibration or other appropriate testing to facilitateoperation of the HVAC system 100 in an efficiency mode which providesincreased cooling capacity, efficiency, and/or comfort during a peakdemand response time.

At step 404, the controller 136 determines whether a measuredtemperature (e.g., a temperature of the conditioned space or thetemperature of a zone or portion of the conditioned space) is within apredefined range of the new temperature setpoint (T_(new)) establishedat step 402. For example, the controller may determine whether themeasured temperature is greater than T_(new)−1° F. and less thanT_(new)+0.5° F. (e.g., as shown in the example of FIG. 3B). If themeasured temperature is not within this range, the controller 136proceeds to step 406 and determines whether the relative humidity of theconditioned space is greater than or equal to the maximum relativehumidity value. If the relative humidity value is greater than or equalto the maximum relative humidity value, the controller 136 proceeds tostep 408 and adjusts the speed of the blower 128 such that the HVACsystem 100 operates at a normal cooling mode CFM/ton value (e.g., ofabout 400 to 450 CFM/ton). Otherwise, if the relative humidity value isnot greater than or equal to the maximum relative humidity value, theHVAC system 100 continues to operate in the efficiency mode associatedwith step 402 (i.e., at the decreased compressor speed and the blowerspeed determined based on the compressor speed).

If at step 404 the measured temperature is within the temperature rangeassociated with this step, the controller 136 proceeds to step 410. Atstep 410, the compressor 106 is increased to a medium speed (e.g., in arange from greater than 30 Hz to about 50 Hz), and a new speed isdetermined for the blower 128. For example, the new speed for the blower128 may be determined based on a predefined relationship, as describedabove. The speed of the blower 128 is adjusted based on this newlydetermined speed. For example, the speed of the blower 128 may beadjusted to the determined speed or to a speed within about 5% of thedetermined speed.

At step 412, the controller determines whether a measured temperature(e.g., a temperature of the conditioned space or the temperature of azone or portion of the conditioned space) is greater than a thresholdtemperature. For example, the threshold temperature may be T_(new)+0.5°F. If the measured temperature is not greater than the thresholdtemperature, the controller 136 proceeds to step 414 and determineswhether a relative humidity associated with the conditioned space isgreater than or equal to the maximum relative humidity value. If therelative humidity is greater than or equal to the maximum relativehumidity value, the controller 136 proceeds to step 416 and adjusts thespeed of the blower 128 such that the HVAC system 100 operates at anormal cooling mode CFM/ton value (e.g., of about 400 to 450 CFM/ton).Otherwise, if the relative humidity is not greater than or equal to themaximum relative humidity value, the HVAC system 100 continues tooperate in the efficiency mode associated with step 410 (i.e., at amedium compressor speed and a blower speed based on the compressorspeed). Returning to step 412, if the measured temperature is greaterthan the threshold temperature, the compressor 106 is set to a highspeed (e.g., a speed greater than 50 Hz), and a speed is determined forthe blower 128 at step 420. The speed of the blower 128 is set based onthe determined speed, as described above.

In some embodiments, steps 404, 410, and 412 may be implemented in amore continuous manner using a feedback control loop 418. For example,proportional-integral (PI) control may be used to implement these stepsof the method 400 such that the speed of the compressor 106 is graduallyadjusted (e.g., increased) during a peak demand response time, based onthe measured temperature, and the speed of the blower 128 is similarlyadjusted (e.g., based on a predefined relationship as described above)to a value determined based on the speed of the compressor 106. Feedbackcontrol loop 418 may facilitate efficient adjustment of the speed of thecompressor 106 and blower 128 to provide improved comfort to aconditioned space during a peak demand response time. For example, thefeedback control loop 418 may facilitate operation of the HVAC system100 at in increased sensible capacity such that the temperature of aconditioned space may be held at a lower temperature for a greaterportion of a peak demand response time than was possible using previoustechnologies.

If the demand request 138 is associated with a requirement to reducepower consumption, the method 400 may begin from step 314 of FIG. 3A atstep 422. At step 422, the speed of the compressor 106 is decreased. Forexample, the compressor 106 may be adjusted to operate in a low speedmode (e.g., at a speed of about 30 Hz or less). A speed is determinedfor the blower 128 based on the decreased blower speed (e.g., asdescribed above), and/or the speed of the blower 128 is adjusted basedon the determined speed. At step 424, the controller 136 determineswhether a measured relative humidity (e.g., a relative humidity of theconditioned space or of a zone of the conditioned space) is greater thanor equal to the maximum relative humidity value. If the relativehumidity value is greater than or equal to the maximum relative humidityvalue, the controller 136 proceeds to step 426 and adjusts the speed ofthe compressor 106 and/or the speed of the blower 128 such that the HVACsystem 100 operates at a normal cooling mode CFM/ton value (e.g., ofabout 400 to 450 CFM/ton). For example, the compressor speed may beincreased to a medium speed value initially (e.g., a speed in a rangefrom greater than 30 Hz to about 50 Hz) before the speed is graduallyincreased to a high speed of greater than 50 Hz (e.g., and up to themaximum recommended compressor speed). Otherwise, if the relativehumidity value is not greater than or equal to the maximum relativehumidity value, the HVAC system 100 continues to operate according tothe efficiency mode associated with step 422.

Modifications, additions, or omissions may be made to method 400depicted in FIG. 4. Method 400 may include more, fewer, or other steps.For example, steps may be performed in parallel or in any suitableorder. While at times discussed as controller 136, HVAC system 100, orcomponents thereof performing the steps, any suitable HVAC system orcomponents of the HVAC system may perform one or more steps of themethod.

Third efficiency mode operation of an HVAC system with a face-splitevaporator

In some embodiments, the cooling unit 116 of the HVAC system 100 shownin FIG. 1 is a face-split evaporator. FIG. 5 shows an illustrativeexample of a face-split evaporator 500. The cooling unit 116 of FIG. 1may be or include the face-split evaporator 500. As shown in FIG. 5, theface-split evaporator 500 includes at least a top evaporator circuit 502and a bottom evaporator circuit 504. Generally, each of the evaporatorcircuits 502 and 504 is associated with a corresponding condensing unit506 and 512, respectively. Condensing unit 506 may include a compressor508 and a condenser 510, and condensing unit 512 may include acompressor 514 and a condenser 516. The one or more condensing units 104of FIG. 1 may include condensing units 506 and 512.

A portion 118 a of the airflow 118 of FIG. 1 may flow through the topcircuit 502 and exit the top circuit 502 as cooled airflow portion 120a. When airflow portion 118 a flows through the top circuit 502, watervapor from airflow 118 a may condense on the coils of the top circuit502. At least a portion of this condensed water may fall on the surface(e.g., the surface of coils) of the bottom circuit 504. Even when thecondensing unit 512 of the bottom evaporator circuit 504 is turned off(i.e., when compressor 514 is turned off), an airflow portion 118 b ofthe airflow 118 may flow through the bottom circuit 504 and beevaporatively cooled via contact with the water received from the topcircuit 502. Evaporatively cooled airflow portion 120 b may exit thebottom circuit 504. Airflow 120 of FIG. 1 may include each of airflows120 a and 120 b of FIG. 5.

In some embodiments, the face-split evaporator 500 is positioned above adrain pan 518 which captures water falling from the evaporator 500(i.e., water not retained on the surface of the bottom circuit 504). Atleast a portion of the water captured in the drain pan 518 may beabsorbed by an air-permeable media 520 and used to provide furtherevaporative cooling of airflow portion 118 b. For example, the media 520may be in fluidic contact with the drain pan 518 via a fluidicconnection 522 or may be inserted directly in a portion of the drain pan518. The fluidic connection 522 may be a channel, tube, a section ofwater-absorbing or water-permeable material (e.g., the same material ora different material to that of the air-permeable media 520) or anyother appropriate element for providing transfer of water from the drainpan 518 to the media 520. At least a portion of airflow 118 a may flowthrough media 520 and contact water on and/or within the media 520,thereby providing further evaporative cooling to the airflow portion 118b and improved cooling to airflow 120 of FIG. 1, even when thecompressor 514 is turned off to conserve power and satisfy requirementsof the demand request 138.

FIG. 6 is a flowchart illustrating example method 600 of operating theHVAC system 100 of FIG. 1 when the cooling unit 116 includes theface-split evaporator 500 of FIG. 5. If the demand request 138 isassociated with a requirement to operate the HVAC system 100 at apredefined setpoint temperature, the method 600 may begin from step 312of FIG. 3A at step 602. At step 602, the temperature setpoint 134 isadjusted to the predefined setpoint temperature associated with thedemand request 138 (as described above for methods 350 and 400), and thecompressor 514 associated with the bottom evaporator circuit 504 isturned off. Turning off compressor 514 allows the bottom evaporatorcircuit 504 to act as an evaporative cooler without requiring additionalpower consumption. For example, water condensate formed on the topevaporator circuit 502 may fall on the surface of the bottom evaporatorcircuit 504 and evaporatively cool airflow 118 b flowing across theotherwise inactive circuit 504, as described above with respect to FIG.5. At step 604, the controller determines whether a measured temperature(e.g., a temperature of the conditioned space or the temperature of azone or portion of the conditioned space) is greater than a thresholdtemperature. For example, the threshold temperature may be T_(new)+0.5°F. If the measured temperature is greater than the thresholdtemperature, the controller 136 proceeds to step 606 and turns on thecompressor 514 associated with the bottom evaporator circuit 504.

If the demand request 138 is associated with a requirement to reducepower consumption, the method 600 may begin from step 314 of FIG. 3A atstep 608. At step 608, the controller 136 turns off the compressor 514associated with the bottom evaporator circuit 504, thereby allowing thebottom evaporator circuit 504 to act as an evaporative cooler withoutconsuming power via operation of compressor 514, as described above withrespect to step 602. If the power consumed by the HVAC system is notdecreased sufficiently to satisfy a percentage of power consumptionassociated with the demand request 138, the controller 138 may furtherdecrease the speed of the compressor 508 and/or of the blower 128. Atstep 610, the controller 136 determines whether a measured relativehumidity is greater than or equal to the maximum relative humidityvalue. If the relative humidity value is greater than or equal to themaximum relative humidity value, the controller 136 proceeds to step 612and turns on the compressor 514 associated with the bottom evaporatorcircuit 504 and turns on the compressor 508 associated with the topevaporator circuit 502. This facilitates operation at a decreased powerconsumption as required by the demand request 138 (i.e., with onecompressor turned off), while preventing a further increase in relativehumidity by no longer providing for substantial evaporative cooling inthe bottom evaporator circuit 514, which was facilitated by shuttingdown the compressor 514 associated with the bottom evaporator circuit504. Otherwise, if the relative humidity value is not greater than orequal to the maximum relative humidity value, the HVAC system 100continues to operate in the efficiency mode with the compressor 514turned off.

Modifications, additions, or omissions may be made to method 600depicted in FIG. 6. Method 600 may include more, fewer, or other steps.For example, steps may be performed in parallel or in any suitableorder. While at times discussed as controller 136, HVAC system 100, orcomponents thereof performing the steps, any suitable HVAC system orcomponents of the HVAC system may perform one or more steps of themethod.

Example Controller

FIG. 7 is a schematic diagram of an embodiment of the controller 136.The controller 136 includes a processor 702, a memory 704, and aninput/output (I/O) interface 706.

The processor 702 includes one or more processors operably coupled tothe memory 704. The processor 702 is any electronic circuitry including,but not limited to, state machines, one or more central processing unit(CPU) chips, logic units, cores (e.g. a multi-core processor),field-programmable gate array (FPGAs), application specific integratedcircuits (ASICs), or digital signal processors (DSPs) thatcommunicatively couples to memory 704 and controls the operation of HVACsystem 100. The processor 702 may be a programmable logic device, amicrocontroller, a microprocessor, or any suitable combination of thepreceding. The processor 702 is communicatively coupled to and in signalcommunication with the memory 704. The one or more processors areconfigured to process data and may be implemented in hardware orsoftware. For example, the processor 702 may be 8-bit, 16-bit, 32-bit,64-bit or of any other suitable architecture. The processor 702 mayinclude an arithmetic logic unit (ALU) for performing arithmetic andlogic operations, processor registers that supply operands to the ALUand store the results of ALU operations, and a control unit that fetchesinstructions from memory 704 and executes them by directing thecoordinated operations of the ALU, registers, and other components. Theprocessor may include other hardware and software that operates toprocess information, control the HVAC system 100, and perform any of thefunctions described herein (e.g., with respect to FIG. 3). The processor702 is not limited to a single processing device and may encompassmultiple processing devices. Similarly, the controller 136 is notlimited to a single controller but may encompass multiple controllers.

The memory 704 includes one or more disks, tape drives, or solid-statedrives, and may be used as an over-flow data storage device, to storeprograms when such programs are selected for execution, and to storeinstructions and data that are read during program execution. The memory704 may be volatile or non-volatile and may include ROM, RAM, ternarycontent-addressable memory (TCAM), dynamic random-access memory (DRAM),and static random-access memory (SRAM). The memory 704 is operable tostore one or more setpoints 708 and threshold values 710.

The one or more setpoints 708 include but are not limited to thetemperature setpoint 134 of FIG. 1. In general, the setpoint(s) 708 mayinclude any temperature, relative humidity, or other setpoints used toconfigure cooling or heating functions of the HVAC system 100 and/oroperation of the HVAC system 100 according to any of the efficiencymodes described in this disclosure. For example, the setpoint(s) mayinclude a predefined setpoint temperature received with or as a part ofthe demand request 138. The threshold values 710 include any of thethresholds used to implement the functions described herein including,for example, the threshold temperatures, maximum relative humidityvalues, and temperature range values described with respect to themethods of FIGS. 3A-B, 4, and 6 above.

The I/O interface 706 is configured to communicate data and signals withother devices. For example, the I/O interface 706 may be configured tocommunicate electrical signals with components of the HVAC system 100including the compressor 106, the expansion valve 114, the blower 128,sensors 130 a-b, and the thermostat 132. For cases where the HVAC systemincludes a face-split evaporator 500 (e.g., as described with respect toFIGS. 5 and 6 above), the I/O interface 706 provides communication withcompressors 508 and 514. The I/O interface may provide and/or receive,for example, compressor speed signals blower speed signals, temperaturesignals, relative humidity signals, thermostat calls, temperaturesetpoints, environmental conditions, and an operating mode status forthe HVAC system 100 and send electrical signals to the components of theHVAC system 100. The I/O interface 706 may include ports or terminalsfor establishing signal communications between the controller 136 andother devices. The I/O interface 706 may be configured to enable wiredand/or wireless communications.

While several embodiments have been provided in the present disclosure,it should be understood that the disclosed systems and methods might beembodied in many other specific forms without departing from the spiritor scope of the present disclosure. The present examples are to beconsidered as illustrative and not restrictive, and the intention is notto be limited to the details given herein. For example, the variouselements or components may be combined or integrated in another systemor certain features may be omitted, or not implemented.

In addition, techniques, systems, subsystems, and methods described andillustrated in the various embodiments as discrete or separate may becombined or integrated with other systems, modules, techniques, ormethods without departing from the scope of the present disclosure.Other items shown or discussed as coupled or directly coupled orcommunicating with each other may be indirectly coupled or communicatingthrough some interface, device, or intermediate component whetherelectrically, mechanically, or otherwise. Other examples of changes,substitutions, and alterations are ascertainable by one skilled in theart and could be made without departing from the spirit and scopedisclosed herein.

To aid the Patent Office, and any readers of any patent issued on thisapplication in interpreting the claims appended hereto, applicants notethat they do not intend any of the appended claims to invoke 35 U.S.C. §112(f) as it exists on the date of filing hereof unless the words “meansfor” or “step for” are explicitly used in the particular claim.

What is claimed is:
 1. A heating, ventilation, and air conditioning(HVAC) system comprising: a variable-speed compressor configured tocompress refrigerant flowing through the HVAC system; a blowerconfigured to provide a flow of air through the HVAC system at acontrollable flow rate; and a controller communicatively coupled to thevariable-speed compressor and the blower, the controller configured to:receive a demand request, the demand request comprising a command tooperate the HVAC system at a predefined setpoint temperature; inresponse to receiving the demand request: adjust a setpoint temperatureassociated with the HVAC system to the predefined setpoint temperature;decrease a speed of the variable-speed compressor to a low-speedsetting, thereby operating the HVAC system at a first tonnage ofcooling, the first tonnage of cooling corresponding to a decreasedtonnage of cooling associated with the decreased speed of thevariable-speed compressor, wherein the low-speed setting corresponds tooperation of the variable-speed compressor at a low speed of about 75%or less of a recommended operating speed of the variable-speedcompressor; and adjust the controllable flow rate of the flow of airprovided by the blower to a first flow rate, based on a predefined ratioof blower flow rate to tonnage of cooling (CFM/ton ratio); wherein,following decreasing the speed of the variable-speed compressor andadjusting the controllable flow rate of the flow of air provided by theblower, a CFM/ton ratio of the HVAC system is greater than or equal to afirst predefined value.
 2. The HVAC system of claim 1, wherein the firstpredefined value is 500 cubic feet per minute per tonnage of cooling. 3.The HVAC system of claim 1, wherein: the demand request comprises astart time associated with the command to operate the HVAC system at thepredefined setpoint temperature; and the controller is furtherconfigured to, prior to adjusting the setpoint temperature to thepredefined setpoint temperature, cause a space conditioned by the HVACsystem to be dehumidified before the start time is reached.
 4. The HVACsystem of claim 1, the controller further configured to: determinewhether a temperature of a space conditioned by the HVAC system iswithin a predefined temperature range encompassing the setpointtemperature; in response to determining the temperature of the space isnot within the predefined temperature range, increase the speed of thevariable-speed compressor to a medium-speed setting, thereby operatingthe HVAC system at a second tonnage, the second tonnage of coolingcorresponding to an increased tonnage of cooling associated with theincreased speed of the variable-speed compressor, wherein a medium speedassociated with the medium-speed setting is greater than the low speedof the low-speed setting; and adjust the controllable flow rate of theflow of air provided by the blower to a second flow rate, such that aratio of the second flow rate to the second tonnage of cooling ismaintained at the first predefined value.
 5. The HVAC system of claim 4,the controller further configured to: determine whether the temperatureof a space conditioned by the HVAC system is greater than a thresholdtemperature; in response to determining the temperature of the space isgreater than a threshold temperature, further increase the speed of thevariable-speed compressor to a high-speed setting, thereby operating theHVAC system at a third tonnage of cooling, the third tonnage of coolingcorresponding to a further increased tonnage of cooling associated withthe further increased speed of the variable-speed compressor, wherein ahigh speed associated with the high-speed setting is greater than themedium speed associated with the medium-speed setting; and adjust thecontrollable flow rate of the flow of air provided by the blower to athird flow rate, such that a ratio of the third flow rate to the thirdtonnage of cooling is decreased to a second predefined value, whereinthe second predefined value is less than the first predefined value. 6.The HVAC system of claim 5, wherein the second predefined value is in arange from about 400 to about 450 cubic feet per minute per tonnage ofcooling.
 7. The HVAC system of claim 1, the controller furtherconfigured to: determine if a relative humidity of a space conditionedby the HVAC system is greater than a predefined maximum relativehumidity value; in response to determining the relative humidity of thespace is greater than the predefined maximum relative humidity value:adjust the speed of the variable-speed compressor, thereby operating theHVAC system at a second tonnage of cooling, the second tonnage ofcooling corresponding to an adjusted tonnage of cooling associated withthe adjusted speed of the variable-speed compressor; and adjust thecontrollable flow rate of the flow of air provided by the blower to asecond flow rate, such that a ratio of the second flow rate to thesecond tonnage of cooling is decreased to a second predefined value,wherein the second predefined value is less than the first predefinedvalue.
 8. The HVAC system of claim 1, wherein the demand request isreceived from a third party.
 9. A method of operating a heating,ventilation, and air conditioning (HVAC) system, the method comprising:receiving a demand request, the demand request comprising a command tooperate the HVAC system at a predefined setpoint temperature; inresponse to receiving of the demand request: adjusting a setpointtemperature associated with the HVAC system to the predefined setpointtemperature; decreasing a speed of a variable-speed compressor of theHVAC system to a low-speed setting, thereby operating the HVAC system ata first tonnage of cooling, the first tonnage of cooling correspondingto a decreased tonnage of cooling associated with the decreased speed ofthe variable-speed compressor, wherein the low-speed setting correspondsto operation of the variable-speed compressor at a low speed of about75% or less of a recommended operating speed of the variable-speedcompressor; and adjusting a controllable flow rate of a flow of airprovided by a blower of the HVAC system to a first flow rate, based on apredefined ratio of blower flow rate to tonnage of cooling (CFM/tonratio); wherein, following decreasing the speed of the variable-speedcompressor and adjusting the controllable flow rate of the flow of airprovided by the blower, a CFM/ton ratio of the HVAC system is greaterthan or equal to a first predefined value.
 10. The method of claim 9,wherein the first predefined value is 500 cubic feet per minute pertonnage of cooling.
 11. The method of claim 9, wherein: the demandrequest comprises a start time associated with the command to operatethe HVAC system at the predefined setpoint temperature; and the methodfurther comprises, prior to adjusting the setpoint temperature to thepredefined setpoint temperature, dehumidifying a space conditioned bythe HVAC system before the start time is reached.
 12. The method ofclaim 9, the method further comprising: determining whether atemperature of a space conditioned by the HVAC system is within apredefined temperature range encompassing the setpoint temperature; inresponse to determining the temperature of the space is not within thepredefined temperature range, increasing the speed of the variable-speedcompressor to a medium-speed setting, thereby operating the HVAC systemat a second tonnage of cooling, the second tonnage of coolingcorresponding to an increased tonnage of cooling associated with theincreased speed of the variable-speed compressor, wherein a medium speedassociated with the medium-speed setting is greater than the low speedof the low-speed setting; and adjusting the controllable flow rate ofthe flow of air provided by the blower to a second flow rate, such thata ratio of the second flow rate to the second tonnage of cooling ismaintained at the first predefined value.
 13. The method of claim 12,the method further comprising: determining whether the temperature of aspace conditioned by the HVAC system is greater than a thresholdtemperature; in response to determining the temperature of the space isgreater than a threshold temperature, further increasing the speed ofthe variable-speed compressor to a high-speed setting, thereby operatingthe HVAC system at a third tonnage of cooling corresponding to a furtherincreased tonnage of cooling associated with the further increased speedof the variable-speed compressor, wherein a high speed associated withthe high-speed setting is greater than the medium speed associated withthe medium-speed setting; and adjusting the controllable flow rate ofthe flow of air provided by the blower to a third flow rate, such that aratio of the third flow rate to the third tonnage of cooling isdecreased to a second predefined value, wherein the second predefinedvalue is less than the first predefined value.
 14. The method of claim13, wherein the second predefined value is in a range from about 400 toabout 450 cubic feet per minute per tonnage of cooling.
 15. The methodof claim 9, the method further comprising: determining if a relativehumidity of a space conditioned by the HVAC system is greater than apredefined maximum relative humidity value; in response to determiningthe relative humidity of the space is greater than the predefinedmaximum relative humidity value: adjusting the speed of thevariable-speed compressor, thereby operating the HVAC system at a secondtonnage of cooling, the second tonnage of cooling corresponding to anadjusted tonnage of cooling associated with the adjusted speed of thevariable-speed compressor; and adjusting the controllable flow rate ofthe flow of air provided by the blower to a second flow rate, such thata ratio of the second flow rate to the second tonnage of cooling isdecreased to a second predefined value, wherein the second predefinedvalue is less than the first predefined value.